Cooling-oil guiding element, and drive train and hybrid module having said cooling-oil guiding element

ABSTRACT

A cooling oil guiding device for a clutch actuatable by an axially movable piston. The piston is radially inward of the clutch, and separates a pressure space and a compensation space. The compensation space is delimited by an axially stationary compensation space cover and a seal cover coupled to the piston. The compensation space cover and the seal cover axially overlap radially outwardly and are axially movable relative to one another via a sealing element. An overflow opening connects the compensation space to an oil channel in the seal cover between the seal cover and the piston, the oil channel opens radially outward. A control edge is provided at a component part axially immovable relative to the piston, by which an oil flow exiting from the oil channel is guided through the clutch when the clutch is closed and is guided past the clutch when the clutch is open.

CROSS REFERENCE TO RELATED APPLICATIONS

This is a U.S. national stage of Application No. PCT/EP2020/060736 filedApr. 16, 2020. Priority is claimed on German Application No. DE 10 2019205 571.0 filed Apr. 17, 2019 the content of which is incorporatedherein by reference.

BACKGROUND OF THE INVENTION 1. Field of the Invention

The present disclosure is directed to a guiding element for cooling oilin a powertrain.

2. Description of Related Art

Various possibilities for distributing cooling oil are known in the art,for example, by selective guiding via closed channels arranged in thehousing or component parts, or distributing by rotating component parts,where the component parts run through an oil sump and/or distributecooling oil which is supplied centrally by centrifugal force. Problemswith the prior art consist in the uncontrolled swirling and uncontrolleddistribution of the cooling oil.

SUMMARY OF THE INVENTION

It is the object of one aspect of the present invention to provide acooling oil guiding element that can selectively distribute the coolingoil.

One aspect of the invention is a cooling oil guiding device and apowertrain and a hybrid module.

According to one aspect of the invention, a cooling oil guiding devicefor a clutch arrangement in which a clutch is provided that can beactuated via a piston movable in axial direction in order to changebetween an actuated position and an open position, the piston isarranged radially inwardly of the clutch, the piston separates apressure space and a compensation space from one another, thecompensation space is delimited by a compensation space cover which isstationary in axial direction, and a seal cover is coupled to thepiston, and the compensation space cover and the seal cover overlapradially outwardly in axial direction and are connected so as to bemovable relative to one another in axial direction via a sealingelement, is characterized in that an overflow opening that connects thecompensation space to an oil channel provided between the seal cover andthe piston is provided in the seal cover, in that the oil channel opensoutward in radial direction, and in that a control edge is provided at acomponent part which is axially immovable relative to the piston, bywhich control edge at least most of an oil flow exiting from the oilchannel is guided through the clutch when the clutch is closed and isguided past the clutch when the clutch is open.

Within the meaning of the present application, a clutch is a mechanismfor mechanically transmitting or disconnecting torque from an input sideto an output side. In particular, a clutch has one or more frictioncomponents which are brought in and out of contact with one another orwith a pressure plate. For example, a clutch can be a single plateclutch, a multiple plate clutch or a cone clutch. The clutch is actuatedby an axially movable piston. In order to move the piston, this pistonhas a pressure space on one side which can be pressurized with a fluid,preferably oil. A compensation space is provided on the other side ofthe piston. In order to ensure problem-free functioning, thecompensation space is filled with oil, preferably without beingpressurized.

The compensation space is partially delimited by a compensation spacecover provided to be fixed in axial direction with respect to theclutch. The compensation space is further delimited by a seal coverconnected to the piston and is movable jointly with the latter. Thecompensation space cover and the seal cover overlap in axial directionso that the compensation space remains closed also during a relativemovement between the compensation space cover and the seal cover. Asealing element is provided between the compensation space cover andseal cover in order to prevent or minimize oil exiting from thecompensation space.

The seal cover and the piston are connected to one another such that anoil channel that opens outward in radial direction is formed between theseal cover and the piston. At least one overflow opening that connectsthe compensation space to the oil channel is provided at the seal cover.The overflow opening ensures that no oil pressure or no excessive oilpressure, in particular no oil pressure elevated above the pressurespace, builds up in the compensation space, and the oil flowing outthrough the overflow opening can be used simultaneously as cooling oilfor further components, for example, the clutch. The overflow openingcan be formed, for example, as an annular gap which extends over theentire circumference or a plurality of orifices distributed over thecircumference.

When the clutch is closed, this clutch is preferably provided withcooling oil in order to ensure that heat is carried off to a sufficientextent to prevent overheating and increased wear. Conversely, when theclutch is open, it is advantageous when no cooling oil or only smallamounts of cooling oil are supplied to the clutch in order to reduce adrag torque resulting from cooling oil present between the frictionelements of the clutch. For this purpose, a control edge is provided atan axially immovable part, this control edge being arranged in axialdirection between the axial end positions of the radially outer openingof the oil channel when the clutch is open or closed. Accordingly, bythe control edge, the oil flow exiting from the oil channel dependentupon centrifugal force can be selectively supplied to the clutch orguided past the clutch to supply other components such as an electricmachine or the like. Depending on the embodiment form, the oil flow canalso be divided by the control edge so that the oil flow is guided pastthe clutch only partially rather than in its entirety. The control edgeis preferably formed as a circumferential inwardly protrudingprojection.

Embodiment forms of a cooling oil guiding device are characterized inthat the control edge is provided at the compensation space cover. Thecontrol edge is advantageously provided at the compensation space coverbecause of the axially fixed arrangement with respect to the clutch andthe spatial proximity of the compensation space cover to the seal coverand, therefore, to the oil channel. As a result of the spatialproximity, it can be ensured that the oil flow can be switchedsubstantially in its entirety by the control edge, since there is onlyminimal expansion or misting, if any, of the oil flow.

Other embodiment forms of a cooling oil guiding device are characterizedin that the control edge is provided at an inner carrier of the clutch.This advantageously facilitates the production of the compensation spacecover and possibly saves weight.

Cooling oil guiding devices according to embodiment forms arecharacterized in that the overflow opening is provided in the radiallyinner area of the seal cover. By providing the overflow opening in theradially inner area, it is ensured that the compensation space issufficiently filled with oil, since the compensation space fills withcentrally supplied oil radially outwardly depending on centrifugalforce.

Embodiment forms of a cooling oil guiding device are characterized inthat the control edge is formed as a radially inwardly protrudingprojection which, at least on one side in axial direction, delimits anannular space with radial through-openings distributed along thecircumference. Because of the radially inwardly protruding projection,the oil flow coming from radially inward is reliably supplied todifferent areas corresponding to the switching position of the piston.An annular space is advantageously provided adjacent to the projection.The supplied cooling oil can be selectively guided to the clutch orfurther component parts via the through-openings in the annular space.

Cooling oil guiding devices according to embodiment forms arecharacterized in that the control edge is provided in an axial end area,or two annular spaces adjacent to one another in axial direction areseparated from one another by the control edge.

It is advantageous for a simpler component geometry when the projectionis provided in an axial end area. In this way, the oil flow can beguided directly radially past the component part in one of the switchingpositions of the piston.

The cooling oil can also be distributed over a greater axial areathrough an annular space or annular spaces, or through-openings thereof,provided on both sides of the projection particularly when the axialspacing of the different positions for supplying the cooling oil thatdepend on the switching position of the piston is greater than the axialstroke of the piston.

Embodiment forms of a cooling oil guiding device are characterized inthat at least one spacer is provided between the seal cover and thepiston, and in that the spacer has at least one continuous cutoutextending in radial direction to form the oil channel. At least onespacer is preferably provided in order to facilitate the positioning ofthe piston and seal cover relative to one another and to reliably keepthe oil channel open in the event of a possible deformation of thecomponent parts, for example, due to pressure. The extension of the oilchannel in axial direction is determined by the spacer. Further, theconnection between the piston and the seal cover can be carried out viathe spacer or spacers. In order to the form the oil channel, the spacerand/or spacers have cutouts therebetween which are radially continuous.

Cooling oil guiding devices according to embodiment forms arecharacterized in that the spacer is provided in the radially outer area.As the result of spacers in the radially outer area, the geometry of theoutlet of the oil channel can be adapted by the spacer if necessary, forexample, in order to achieve the least possible expansion of the exitingoil flow so as to facilitate the separation by the control edge.

A further aspect of the present application is a powertraincharacterized in that a clutch arrangement is provided with a coolingoil guiding device according to one of the embodiment forms describedherein.

Another aspect of the present application is a hybrid module for apowertrain, characterized in that a clutch arrangement is provided witha cooling oil guiding device according to the description, and in that acontrol edge is provided at a component part which is axially immovablerelative to the piston, by which control edge an oil flow exiting fromthe oil channel is guided at least for the most part through the clutchwhen the clutch is closed and past the clutch when the clutch is open aswell as to a rotor of an electric machine of the hybrid module.

Embodiment forms of a cooling oil guiding device for rotating componentparts, for example, in a clutch device, wherein an annular oil channelextends in radial direction, and wherein cooling oil can be suppliedfrom radially inward and the oil channel is partially open radiallyoutwardly, are characterized in that a sealing area is provided in aradially outer area of the oil channel, in that the sealing area hasblocking elements and outlet elements, in that the blocking elements arearranged radially inwardly of the outlet elements and have at least twopassages in radial direction which are distributed along thecircumference, in that outlet channels which are aligned with thepassages and inlets which are disposed between the outlet channels incircumferential direction are formed by the outlet elements, and in thatan annular channel is provided between the blocking elements and theoutlet elements in order to connect the inlets with the outlet channelsand passages, respectively.

Oil is often guided via a shaft or hub at rotating component parts,particularly in the area of a powertrain of a vehicle. An oil channel isneeded, for example, in order to route oil to surrounding componentparts for cooling. In many cases, however, a selective routing of thecooling oil is advantageous because otherwise oil possibly reachescomponent parts which are not to be supplied with oil or should only besupplied with small amounts of oil. The outlet of cooling oil can beshifted farther radially outward by an oil channel arranged annularlyaround the rotating component part.

In order for the cooling oil to exit in a defined manner, a sealing areais provided in the radially outer area of the oil channel. The sealingarea comprises a plurality of blocking elements which are providedcircumferentially, preferably on a diameter, and passages having adefined cross section are formed between the blocking elements. Theamount of cooling oil can be defined through the passages, in particularthrough the quantity and cross section thereof.

The blocking elements are radially outwardly surrounded by outletelements. The outlet elements define outlet channels in radial directionwhich are aligned with the passages. The cooling oil can be selectivelydelivered radially outward to surrounding component parts via the outletchannels. In addition, inlets which are arranged in circumferentialdirection between the outlet channels are defined by the outletelements. There are at least half as many inlets as outlet channels, andup to a multiple of inlets, particularly twice as many, can also beprovided. Preferably, an equal amount of outlet channels and inlets canbe provided.

An annular channel that connects the inlets with the outlet channelsand, therefore, also the passages is provided between the blockingelements and the outlet elements. At least one inlet is connected withat least one outlet channel by the annular channel in each instance.This also means that an inlet is connected to a plurality of outletchannels and/or an outlet channel is connected to a plurality of inlets.An advantageous embodiment example provides an annular channelsurrounding the entire circumference.

Because of the cooling oil exiting the outlet channels, a negativepressure is formed radially inwardly. In order to prevent a swirling ofthe cooling oil due to the negative pressure, inlets are provided viawhich an atmosphere such as air surrounding the rotating component partcan flow in so as to equalize the negative pressure. The in-flowing airexits from the outlet channel together with the cooling oil.Accordingly, a kind of centrifugal pump effect takes place.

Embodiment forms of a cooling oil guiding device are characterized inthat the cross section of the passages decreases radially outward inradial direction. Due to the physical forces acting on the oil flow, theoil flow would be atomized or swirled after the passages (expansion dueto higher diameter-dependent velocity). In order to prevent this, thepassages are formed to narrow in diameter in radial direction. Thisprevents an expansion of the oil flow. Therefore, the oil flow entersthe outlet channel with extensively laminar flow.

Cooling oil guiding devices according to embodiment forms arecharacterized in that the cross section of the outlet channels decreasesoutward in radial direction. In addition to the air flowing in via theinlets for equalizing the occurring negative pressure, the outletchannels can be additionally provided with a cross section which narrowsin diameter outward. As with the above-described passages, an expansionof the oil flow can be counteracted by the preferably continuouslyreduced cross section. This leads to an oil flow which exits from theoutlet channel with a flow that is as laminar as possible. Accordingly,a swirling or atomization of the oil flow is reduced or prevented sothat a defined feed is facilitated or is made possible.

Embodiment forms of a cooling oil guiding device are characterized inthat the outlet channels have a tear-off edge at their radially outerrim on at least one side, this tear-off edge having an angle of lessthan or equal to 90°. In order to minimize the expansion of the oil flowas far as possible as it exits from the outlet channel, a tear-off edgeis provided on at least one side of the outer rim of the outlet channel.The tear-off edge is preferably provided at a plurality of, particularlyall, sides of the radially outer rim of the outlet channel. As a resultof the tear-off edge, the oil flow detaches directly from the wall ofthe outlet channel and an oil flow which is as laminar as possible ismaintained with little or no expansion. In order for the flow to detach,the tear-off edge has an acute angle of less than or equal to 90°.

Cooling oil guiding devices are characterized in embodiment forms inthat the inlets have a radius at their radially outer rim on at leastone side. For the in-flowing air, on the other hand, it is advantageousthat the edges of the radially outer rim of the inlets are rounded. Dueto the rounded inlets, a more uniform flow of air is achieved, andturbulence in the air flow is reduced.

Embodiment forms of a cooling oil guiding device are characterized inthat the outlet elements are rounded at the side thereof facing theannular channel so that an air flow from the inlets via the annularchannel to the outlet channels is kept as laminar as possible.Additional swirling of the oil flow due to a turbulent air flow can beprevented or reduced by keeping the air flow as laminar as possible andpreventing turbulence.

Embodiment forms of a cooling oil guiding device are characterized inthat the blocking elements have guiding elements at the passages, whichguiding elements protrude radially into the annular channel in order toguide an air flow in the annular channel in direction of the outletchannels. The air flowing in via the inlets should exit again togetherwith the oil flow via the outlet channels. In order to guide the airflow in a corresponding manner and minimize turbulence, guiding elementsare provided which project into the annular channel. The guidingelements change the direction of the open cross section of the annularchannel in direction of the outlet channel, preferably continuously.

A further aspect of the present application is a powertrain of a vehiclewhich is characterized in that a cooling oil guiding device is providedin accordance with the description. Cooling oil can be selectivelydistributed by a cooling oil guiding device of this kind.

Embodiment forms of a powertrain are characterized in that the coolingoil guiding device is provided in a hybrid module. A reliable supply ofcooling oil is important particularly in a hybrid module in which, forexample, an electric machine enclosing rotating component parts must becooled. This can be ensured by a cooling oil guiding device according toone aspect of the invention.

Powertrains according to embodiment forms are characterized in that thecooling oil guiding device is provided in a clutch arrangement. Wetclutches in particular require a reliable supply of cooling oilespecially in actuated state. This can be ensured by a cooling oilguiding device according to the invention.

BRIEF DESCRIPTION OF THE DRAWINGS

The invention will be explained in more detail with reference to thefigures. Like or similar component parts are designated with consistentreference numerals. In particular, the figures show:

FIG. 1A is a cooling oil guiding device with open clutch;

FIG. 1B is the cooling oil guiding device according to FIG. 1 a withclosed clutch;

FIG. 2A is a cooling oil guiding device with open clutch;

FIG. 2B is the cooling oil guiding device according to FIG. 2 a withclosed clutch;

FIG. 3 is a piston with seal cover;

FIG. 4 is a section along A-A of FIG. 3 .

DETAILED DESCRIPTION OF THE PRESENTLY PREFERRED EMBODIMENTS

FIGS. 1 a, 1 b, 2 a and 2 b show a section of a hybrid module for apowertrain with embodiment examples of a cooling oil guiding device ofwhich primarily the component parts of a clutch arrangement are shown.In view of the extensively rotationally symmetrical construction, onehalf is shown.

The clutch arrangement comprises a clutch 1 that can be constructed inparticular as a friction clutch. In the present example, the input sideof the clutch 1 is connected to an inner carrier 8. The inner carrier 8is connected to an input shaft. The output side of the clutch 1 isconnected to a rotor carrier 17 in the depicted embodiment example. Arotor 11 of an electric machine is provided on the rotor carrier 17, andthe rotor carrier 17 is connected in the depicted embodiment example toa housing of a torque converter; other constructions in which, forexample, the rotor carrier is directly connected to an output shaft orintermediate shaft are also possible.

An axially movable piston 2 is provided for actuating the clutch 1. Forpressure to act upon the piston 2, a pressure space D is provided whichis delimited in the depicted embodiment example by the piston 2, thehousing of the torque converter, a seal arranged therebetween and anintermediate shaft connected to the housing and which can be acted uponby oil pressure through the intermediate shaft. A compensation space Gis located axially opposite the pressure space D with respect to thepiston 2. The compensation space G is likewise supplied with oil inorder to lubricate the component parts and equalize an oil pressure inthe pressure space D in the unpressurized state. In the depictedembodiment example, an elastic restoring element such as one or moresprings is also provided for the piston 2 in the compensation space G,by which the piston 2 is restored to its initial position, in this casean open position, in the unpressurized state.

In the depicted embodiment example, the compensation space G isdelimited by the intermediate shaft, via which the supply of oil is alsocarried out, a compensation space cover 3 connected to the intermediateshaft, and the piston 2 and a seal cover 4, respectively, which isconnected to the piston 2. A sealing element 5 which abuts thecompensation space cover 3 is provided at the seal cover 4.

Together with the piston 2, the seal cover 4 encloses an oil channel Kextending substantially in radial direction. An overflow opening 6connecting the compensation space G to the oil channel K is provided atthe radially inner end of the seal cover 4. The overflow channel 6 canbe constructed as a circumferential annular gap or formed by one or morecutouts distributed along the circumference. The oil channel K is openat its radially outer end in order to deliver exiting oil as cooling oilto the radially surrounding component parts.

An oil flow dependent upon the cooling oil guiding device is representedby arrows in the figures.

The basic construction described is the same for all of the depictedembodiment examples, particularly FIGS. 1 a, 1 b, 2 a and 2 b , althoughother embodiment forms are possible.

FIG. 1 a shows the embodiment example in an unactuated state of theclutch 1 in which the piston 2 is not acted upon by pressure.

The compensation space cover 3 in the depicted example has at theradially outer end a portion which extends in axial direction toward thepiston 2. A radially inwardly protruding control edge 7 is provided inthe axial end area of the compensation space cover 3, this control edge7 being arranged in the area of the oil channel K, preferably in theadjacent area in axial direction around the seal cover 4. Accordingly,at least the majority of the oil flow is guided past the compensationspace cover 3 and, therefore, past the clutch 1 which radially surroundsthe compensation space cover 3. In the unactuated state, the clutch 1does not require a supply of cooling oil. Because no cooling oil or onlysmall amounts of cooling oil are supplied, a drag torque occurringbetween the input side and the output side of the clutch 1 is preventedor at least reduced so that losses can be reduced.

In the depicted embodiment example of a hybrid module, the oil flow isguided past the clutch 1 to the rotor 11 of an electric machine thatsurrounds the clutch arrangement in order to ensure cooling thereof. Acooling of the electric machine is required regardless of whether or nota drive such as an internal combustion engine connected to the inputside of the clutch 1 is connected to the further drivetrain via theclutch 1. In the depicted embodiment example, the cooling oil impingeson a rotor carrier 17 for the rotor 11 of the electric machine and isconveyed by the rotor carrier 17 so as to be distributed over the axialextension of the rotor 11.

FIG. 1 b corresponds to the embodiment example according to FIG. 1 a inwhich the clutch 1 is shown in an actuated state. The piston 2 isdisplaced into its actuated position by the pressure space D which isacted upon by pressure. Along with this, the oil channel K is alsodisplaced in axial direction relative to the compensation cover 3 andthe control edge 7 provided at the latter.

Therefore, the oil flow impinges on the compensation space cover 3 andis guided by the control edge 7 in direction of an annular space whichis provided at the compensation space cover 3 adjacent to the controledge 7. Through-openings 9 via which the cooling oil can be guided toradially surrounding component parts are provided at the compensationspace cover 3 in the area of the annular space. In the depictedembodiment example, the cooling oil is guided through thethrough-openings 9 to the inner carrier 8 of the clutch 1 and directedfrom the inner carrier 8 through the clutch 1. After the clutch 1, thecooling oil is routed from the rotor carrier 17 to the electric machine,in particular to the rotor 11.

Accordingly, by the control edge 7, the oil flow is selectivelyconducted in the desired axial direction and prevented from flowing offinto other areas. Depending on the position of the control edge 7,embodiment forms are also possible in which, particularly when there isa significantly widening gush of the oil flow, the oil flow is dividedby the control edge 7 in order to supply all of the component parts withcooling oil in a constant manner but so as to change the distributedamount depending on the switching position of the piston 2.

FIGS. 2 a and 2 b show a further embodiment example of the cooling oilguiding device. The basic construction is identical to that in theembodiment example in FIGS. 1 a and 1 b . Also, FIG. 2 a and FIG. 2 bshow an unactuated state and an actuated state, respectively, of thepiston 2 and clutch 1. The difference consists in that the compensationspace cover 3 does not have any area lengthened axially in direction ofthe piston 2; rather, the control edge 7 is provided at the innercarrier 8 of the clutch 1.

The control edge 7 in FIGS. 2 a and 2 b is likewise similarly arrangedin an axial area which is adjacent to the outlet of the oil channel K inthe movement direction of the piston 2. In this way, the oil flow can becorrespondingly guided past the clutch 1 or through the clutch 1 similarto the description above referring to FIGS. 1 a and 1 b.

FIG. 3 shows a piston 2 with seal cover 4 according to an embodimentexample. Similar to FIGS. 1 a, 1 b, 2 a and 2 b , a sealing element 5 isprovided at the seal cover 4 so as to seal off a compensation space G.An overflow opening 6 is provided radially inwardly, and cooling oil canflow through this overflow opening 6 into the oil channel 6 formedbetween the seal cover 4 and piston 2. In order to ensure that the oilchannel K is kept open during operation, spacers 10 are provided in thedepicted example, since deformation can come about as a result of forcesoccurring during operation.

As is shown, the spacers 10 can be arranged in the radially outer area.However, embodiment forms in which the spacers 10 are provided atdifferent positions are also possible. In other possible embodimentforms, the spacers 10 extend substantially over the radial extension ofthe seal cover 4, or a plurality of spacers 10 are provided on variousdiameters.

As is shown in FIG. 3 , the spacers 10 can be arranged integral with orin conjunction with the sealing element 5. Alternatively oradditionally, the spacers 10 can also be formed by a separate componentpart or by shaped portions at the seal cover 4 and/or piston 2 andcombinations thereof. The spacers 10 must make the oil channel Kpossible. For this reason, the spacers 10 may not be formed incircumferential direction as a ring closed via the thickness of the oilchannel K in order to provide a radially continuous oil channel K.

In the depicted embodiment example, a tear-off edge 15 is provided atthe outer end of the oil channel K. The tear-off edge 15 is provided sothat the oil flow exiting from the oil channel K flows out so as to beas laminar as possible and so that an expansion or swirling and mistingof the cooling oil is prevented or at least reduced. The oil flow canalso possibly be offset or deflected somewhat in axial direction by thetear-off edge 15.

The clear width of the oil channel K in axial direction depends amongother things on the amount of cooling oil to be delivered. The clearwidth is preferably in the range of 0.5 mm to 2 mm. Embodiment formswith a greater clear width, for example, 3 mm or 4 mm, are alsopossible.

FIG. 4 shows a partial area of a section according to line A-A in FIG. 3, which shows the spacers 10 and the outer area of the oil channel K.

Viewed from radially inside, the spacers 10 have blocking elements 12and outlet elements 13. The blocking elements 12 are providedcircumferentially and block an inner area of the oil channel K towardthe outside. At least one passage 14 or, as in the depicted example, aplurality of passages 14 which are preferably uniformly distributed overthe circumference are provided between the blocking elements 12. Theamount of exiting cooling oil can be limited by the passages 14.

In the embodiment example, a plurality of outlet elements 13 areprovided in the radially outer rim of the oil channel K so as to bedistributed over the circumference. The outlet elements 13 are adjacentto one another to form outlet channels A and inlets E. The outletchannels A are preferably arranged to be aligned with the passages 14.The inlets E are arranged in circumferential direction between theoutlet channels A. The quantity of inlets E is at least one half of aquantity of outlet channels A or a multiple thereof. The quantity ispreferably equal as in the depicted example. The inlets E are opposedradially inwardly by a blocking element 12. An annular channel R whichconnects at least one inlet E with an outlet channel A is providedbetween blocking elements 12 and the outlet elements 13. In the depictedexample, the annular channel R extends circumferentially.

In the depicted embodiment example, guiding elements 16 which reduce thecross section of the passages 14 outwardly in radial direction areprovided at the blocking elements 12 to prevent an expansion of thecooling element. The guiding elements 16 prevent an atomization of thecooling oil as it passes from passage 14 into outlet channel A, and anextensively laminar flow of the oil flow is maintained.

The oil flow is conveyed radially outward by the rotation of thecomponent parts. Due to the increasing diameter, the conveyed volume ofthe oil flow generates a negative pressure which, in a free annular gap,leads to undefined intake of surrounding atmosphere such as air andmixing of this air with the oil so that swirling and misting of theexiting oil is increased. In order to prevent this, inlets E areprovided through which air can flow inward. The air is selectivelysupplied to the outlet channel A via the annular channel R connected tothe inlet E. As a result, the cooling oil flowing into the passage 14 ismixed with the sucked in air without resulting in substantial swirling.

The oil flow is shown in FIG. 4 by arrows similar to FIGS. 1 a, 1 b, 2 aand 2 b . Additionally, the flow of sucked in air is represented in FIG.4 by dashed arrows.

Proceeding radially outward, the cross section of the outlet channel Achanges in such a way that a compression of the exiting oil flow isextensively prevented, since this would otherwise lead to an expansionand, therefore, a significant swirling or misting of the oil flow afterexiting from the oil channel K. The cross-sectional course preferablychanges continuously so that an oil flow which is extensively laminar isobtained.

Additionally, tear-off edges 15 are provided in the depicted embodimentexample at the end of the outlet channel A in order to reduce or preventswirling and retain a laminar oil flow. Swirling of the oil flow shouldbe prevented if possible especially in direction of the clutch 1 becausethis would lead to an uncontrolled amount of cooling oil which possiblyresults in an increased drag torque.

The tear-off edge 15 can extend in circumferential direction as in FIG.3 and/or in axial direction as in FIG. 4 . As is shown, the tear-offedge 15 can be produced preferably in one part, although other variantsare also possible. The edges at the inlets E are preferably rounded toallow the air to flow in as uniformly as possible.

The invention is not limited to the described embodiments. As statedabove, only individual advantageous features may be provided or variousfeatures of different examples may be combined with one another.

Thus, while there have shown and described and pointed out fundamentalnovel features of the invention as applied to a preferred embodimentthereof, it will be understood that various omissions and substitutionsand changes in the form and details of the devices illustrated, and intheir operation, may be made by those skilled in the art withoutdeparting from the spirit of the invention. For example, it is expresslyintended that all combinations of those elements and/or method stepswhich perform substantially the same function in substantially the sameway to achieve the same results are within the scope of the invention.Moreover, it should be recognized that structures and/or elements and/ormethod steps shown and/or described in connection with any disclosedform or embodiment of the invention may be incorporated in any otherdisclosed or described or suggested form or embodiment as a generalmatter of design choice. It is the intention, therefore, to be limitedonly as indicated by the scope of the claims appended hereto.

The invention claimed is:
 1. A cooling oil guiding device for a clutcharrangement, comprising: a piston that is axially moveable; a clutchthat can be actuated via the piston to change between an actuatedposition and an open position, wherein the piston is arranged radiallyinwardly of the clutch; a sealing element a compensation space coverthat is stationary in axial direction; a seal cover which is coupled tothe piston, wherein the compensation space cover and the seal coveroverlap radially outwardly in axial direction and are connected to bemovable relative to one another in axial direction via the sealingelement; a compensation space delimited by the compensation space coverand the seal cover; a pressure space that is separated from thecompensation space by the piston; an oil channel is provided in the sealcover that opens outward in radial direction and arranged between theseal cover and the piston; an overflow opening that connects thecompensation space to the oil channel; and a control edge configured asa radially inner projection that extends inward from the compensationspace cover that is axially immovable relative to the piston by at leastpart of an oil flow exiting from the oil channel is guided through theclutch with force when the clutch is closed and is guided past theclutch when the clutch is open.
 2. The cooling oil guiding deviceaccording to claim 1, wherein the overflow opening is provided in aradially inner area of the seal cover.
 3. The cooling oil guiding deviceaccording to claim 1, further comprising: at least one spacer providedbetween the seal cover and the piston, wherein the at least one spacerhas at least one continuous cutout extending in radial direction to formthe oil channel.
 4. The cooling oil guiding device according to claim 3,wherein the at least one spacer is provided in a radially outer area ofthe seal cover.
 5. A cooling oil guiding device for a clutcharrangement, comprising: a piston that is axially moveable; a clutchthat can be actuated via the piston to change between an actuatedposition and an open position, wherein the piston is arranged radiallyinwardly of the clutch; a sealing element a compensation space coverthat is stationary in axial direction; a seal cover which is coupled tothe piston, wherein the compensation space cover and the seal coveroverlap radially outwardly in axial direction and are connected to bemovable relative to one another in axial direction via the sealingelement; a compensation space delimited by the compensation space coverand the seal cover; a pressure space that is separated from thecompensation space by the piston; an oil channel is provided in the sealcover that opens outward in radial direction and arranged between theseal cover and the piston; an overflow opening that connects thecompensation space to the oil channel; and a control edge provided at acomponent part that is axially immovable relative to the piston by atleast part of an oil flow exiting from the oil channel is guided throughthe clutch when the clutch is closed and is guided past the clutch whenthe clutch is open, wherein the control edge is formed as a radiallyinwardly protruding projection which, at least on one side in axialdirection, delimits an annular space with radial through-openingsdistributed along a circumference.
 6. The cooling oil guiding deviceaccording to claim 5, wherein the control edge is provided at least oneof: in an axial end area, and two annular spaces adjacent to one anotherin axial direction and separated from one another by the control edge.7. A powertrain, comprising: a clutch arrangement comprising: a coolingoil guiding device for the clutch arrangement, comprising: a piston thatis axially moveable; a clutch that can be actuated via the piston tochange between an actuated position and an open position, wherein thepiston is arranged radially inwardly of the clutch; a sealing element acompensation space cover that is stationary in axial direction; a sealcover which is coupled to the piston, wherein the compensation spacecover and the seal cover overlap radially outwardly in axial directionand are connected to be movable relative to one another in axialdirection via the sealing element; a compensation space delimited by thecompensation space cover and the seal cover; a pressure space that isseparated from the compensation space by the piston; an oil channel isprovided in the seal cover that opens outward in radial direction andarranged between the seal cover and the piston; an overflow opening thatconnects the compensation space to the oil channel; and a control edgeconfigured as a radially inner projection that extends inward from thecompensation space cover that is axially immovable relative to thepiston by at least part of an oil flow exiting from the oil channel isguided through the clutch with force when the clutch is closed and isguided past the clutch when the clutch is open.
 8. A hybrid module for apowertrain, comprising: a rotor of an electric machine of the hybridmodule; and a cooling oil guiding device for a clutch arrangement,comprising: a piston that is axially moveable; a clutch that can beactuated via the piston to change between an actuated position and anopen position, wherein the piston is arranged radially inwardly of theclutch; a sealing element a compensation space cover that is stationaryin axial direction; a seal cover which is coupled to the piston, whereinthe compensation space cover and the seal cover overlap radiallyoutwardly in axial direction and are connected to be movable relative toone another in axial direction via the sealing element; a compensationspace delimited by the compensation space cover and the seal cover; apressure space that is separated from the compensation space by thepiston; an oil channel is provided in the seal cover that opens outwardin radial direction and arranged between the seal cover and the piston;an overflow opening that connects the compensation space to the oilchannel; and a control edge configured as a radially inner projectionthat extends inward from the compensation space cover that is axiallyimmovable relative to the piston by at least part of an oil flow exitingfrom the oil channel is guided through the clutch with force when theclutch is closed and is guided past the clutch when the clutch is open.